JP4789166B2 - Rotary electric razor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rotary electric razor having an inner blade rotating around a horizontal axis, and more particularly to an electric razor in a form in which motor power is transmitted to an inner blade via a winding transmission.
[0002]
[Prior art]
A rotary electric shaver is known, for example, in Japanese Patent Laid-Open No. 2000-42264. There, the motor power is transmitted to the inner blade via two gear groups. Specifically, the first gear group that rotates about the vertical axis transmits the motor power to one side of the razor head, and the second gear that rotates about the horizontal axis between the final gear and the inner blade of the first gear group. A group is provided.
[0003]
[Problems to be solved by the invention]
As described above, in the power transmission mechanism that transmits the motor power to the inner blade via both the first and second gear groups, the back-crash generated in the meshing portion of each gear, or between the gear and the gear support shaft. The generation of gear noise due to a slight idle gap cannot be avoided. All gears are housed inside the razor head, but the first gear chamber that houses the first gear group and the second gear chamber that houses the second gear group are arranged in an L shape in a state of communicating with each other. It is. Therefore, it is inevitable that gear noise leaks from the second gear chamber to the outside, and gear noise on the first gear chamber side reverberates on the peripheral wall of the second gear chamber, further increasing the sound pressure level of the noise. .
[0004]
The inventors of the present invention are studying to reduce the noise of the rotary electric shaver by reducing the gear noise as described above. Specifically, it is considered to reduce the sound pressure level of gear noise by using a winding transmission mechanism having a timing belt as a transmission element instead of the previous gear group. Incidentally, it is known in Japanese Utility Model Publication No. 55-15802 that motor power is transmitted to the inner blade through a winding transmission mechanism. There, the motor central axis is arranged parallel to the inner cutter central axis, pulleys are fixed to the motor output shaft and the inner cutter axis, and belts are wound around these pulleys. The bearing that supports the inner blade shaft is supported by a leaf spring so that it can move up and down, and a tension roller is placed inside the belt transition locus to absorb slack in the belt when the inner blade moves up and down. ing.
[0005]
As described above, in the transmission structure that transmits the motor power to the inner blade only through the winding transmission mechanism, although the transmission noise due to the gear can be reduced, the motor rotation speed greatly varies due to slight load fluctuations during shaving. It is easy and can not cut the beard in a stable state. Using a high-torque, high-power motor can suppress fluctuations in the rotational speed to some extent, but is expensive. Also, during high-load operation such as when shaving long hair or a tight beard, the belt slips and the driving speed of the inner blade is lowered, so that the sharpness is lowered and it is difficult to put it to practical use.
[0006]
The tension roller to absorb the belt slack is located inside the belt transition locus, so that when the tension roller is tensioning the belt, the belt wrap angle against the pulley can be prevented from decreasing. Therefore, the belt is likely to slip. Since the inner blade, the motor, and the belt mechanism are accommodated in the same case, there is a disadvantage that fouls adhere to the belt and easily slip.
[0007]
An object of the present invention is to provide a rotary electric razor capable of realizing noise reduction of a power transmission mechanism by transmitting motor power to an inner blade via a winding transmission mechanism. Another object of the present invention is to provide a rotary electric shaver that can eliminate transmission loss such as slip in the winding transmission mechanism, improve the driving force of the inner blade, and improve the sharpness. Another object of the present invention is to provide a rotary electric shaver that can reduce the space occupied by the winding transmission mechanism by devising the arrangement of the pulleys and that can optimize the function of the tension pulley. Another object of the present invention is to provide a rotary electric shaver that can eliminate a decrease in transmission efficiency due to the elongation of the timing belt and can easily replace the belt after the endurance period. Another object of the present invention is to transmit the motor power to the inner blade in combination with the gear transmission mechanism and the winding transmission mechanism, thereby realizing a reduction in noise of the power transmission mechanism and accompanying fluctuations in load during shaving. It is a rotary type that suppresses large fluctuations in the motor speed and can reduce the fluctuation range of the motor speed even during high-load operation, such as when shave long hairs or stiff hairs. To provide an electric razor.
[0008]
[Means for Solving the Problems]
The electric razor of the present invention is provided with an inner blade 9 that is driven to rotate about a horizontal axis in the razor head 2 at the top of the main body case 1, and a motor is provided in a transmission chamber 28 provided on one side of the razor head 2. A winding transmission mechanism H that transmits power to the inner blade 9 is accommodated. Winding transmission mechanism H includes a driving pulley 52 and the driven pulley 54, arranged in lower and upper power transmission chamber 28, and wound around the timing belt 55 to the both pulleys 52, 54, arranged on the slack Mi side of the timing belt 55 And the tension mechanism T. The tension mechanism T includes a tension roller 58 that contacts the outer surface of the timing belt 55, a roller support 57 that rotatably supports the tension roller 58, and a spring 59 that moves and urges the tension roller 58. A tension roller 58 is urged and moved by a spring 59 in a direction in which the slack side of the timing belt 55 is deformed into an inner recess. The pulley shaft 60 of the driving pulley 52 is arranged so as to be biased toward the tension side of the timing belt 55 from a vertical plane passing through the center of the pulley shaft 68 of the driven pulley 54. A roller support 57 is disposed between the slack side of the timing belt 55 and the peripheral wall of the transmission chamber 28.
[0011]
A tension roller 58 is supported on one end of the roller support 57 so as to be freely rotatable. The roller support 57 is swingably supported by a shaft 70 provided in the transmission chamber 28 and is urged to swing toward the timing belt 55 by a spring 59.
[0012]
A stopper 71 is provided on the peripheral wall of the transmission chamber 28 to restrict the movement of the tension roller 58 in the belt tension direction. The limit of movement of the tension roller 58 in the belt tension direction by the stopper 71 is set so as to be biased toward the tight side of the timing belt 55 from the rotation position in the free state of the timing belt 55 in the stopped state.
[0013]
A gear group G for transmitting the motor power to the winding transmission mechanism H is accommodated in a transmission chamber 27 provided in the lower part of the razor head 2. The transmission chamber 27 that accommodates the gear group G and the transmission chamber 28 that accommodates the winding transmission mechanism H are hermetically divided by a partition wall 29 provided between the chambers 27 and 28. Are provided between a plurality of spur gears G1 to G4 decelerating and the final gear G4 of the gear group G and the intermediate shaft 44, and the rotational power of the final gear G4 is converted to rotational power around the intermediate shaft 44. It is comprised with a pair of turning gear 45 * 46 converted into. A driving pulley 52 is fixed to an intermediate shaft 44 that penetrates the partition wall 29.
[0014]
The transmission chamber 28 is defined by a partition wall 29 of the motor base 22 and a side wall 33 of the head frame 23, and a cover 34 that covers the outer surfaces of the partition wall 29 and the side wall 33. A flange 62 that restricts the movement of the timing belt 55 in the axial direction is detachably mounted on the pulley shaft 60 that projects from the outer surface of the driving pulley 52. The restriction boss 63 provided on the inner surface of the cover 34 holds and holds the flange 62 so that it cannot be removed.
[0015]
The shaft 70 projects integrally on the outer surface of the side wall 33 that defines the transmission chamber 28. A roller support 57 arranged between the driving pulley 52 and the driven pulley 54 is supported upright by the shaft 70 so as to be swingable back and forth.
[0016]
[Effects of the invention]
In the present invention, since a transmission structure for transmitting the motor power to the inner blade 9 via the winding transmission mechanism H is adopted, the winding transmission is compared with the conventional electric razor in which the motor power is transmitted to the inner blade only by the gear group. The sound pressure level of the gear noise can be reduced by the amount corresponding to the mechanism H, and the noise reduction of the rotary electric shaver can be realized.
[0017]
As shown in FIG. 1, the tension roller 58, the roller support 57, and the spring 59 constitute a tension mechanism T, and the tension roller 58 is moved in the direction in which the slack side transition locus of the timing belt 55 is deformed in an indented shape. 59, when the load suddenly increases and the timing belt 55 swells outwardly on the slack side, the tension mechanism T causes the timing belt 55 to have a winding angle of the driving side and the driven side. Since both the pulleys 52 and 54 are pressed in an increasing direction to suppress the forward movement, the slippage of the timing belt 55 is reliably prevented as compared with the case where a tension mechanism is provided inside the belt trajectory. Thus, power transmission can be reliably performed when the load suddenly increases. Therefore, even when the load fluctuates, the motor power can be reliably transmitted to the inner blade 9 to maintain sharpness.
[0018]
As described above, in the electric razor of the present invention, the tension mechanism T is disposed outside the slack side transition locus of the timing belt 55. Therefore, a space for accommodating the tension mechanism T is indispensable in the transmission chamber 28 in addition to the space determined by the rotation position of the timing belt 55. In general, the centers of the pulley shafts 60 and 68 are positioned on a vertical plane. However, the tension mechanism T protrudes greatly to one side of the winding transmission mechanism H, and an extra storage space is required accordingly. . That is, it is inevitable that a part of the peripheral wall of the transmission chamber 28 protrudes to the front or back of the razor head. In order to eliminate such a situation, to reduce the occupied space of the winding transmission mechanism H, and to further simplify the appearance of the razor head, the pulley shaft 60 of the driving pulley 52 is replaced with the pulley shaft of the driven pulley 54. The tension mechanism T is arranged so as to be biased toward the tension side of the belt transition locus from the vertical plane passing through the center of the belt 68 so as to avoid the tension mechanism T from protruding greatly to one side of the winding transmission mechanism H.
[0019]
The roller support 57 reciprocates with respect to the timing belt 55 to absorb the slack of the belt and adjust the tension. As long as that is the case, the roller support 57 can absorb the slack of the belt in any displacement form such as a linear or arcuate slide displacement or swing displacement. However, if one end of the roller support 57 is swingably supported by the shaft 70, the adjustment operation of the tension roller 58 with respect to fluctuations in the transition trajectory of the timing belt 55 is made smoother than in the case of taking other displacement forms, It is possible to follow quickly without causing a response delay, and the motor power can be reliably transmitted by that amount to improve the driving force of the inner blade.
[0020]
The tension mechanism T can eliminate transmission loss such as slip as the pressing force against the timing belt 55 increases. However, if the belt tension force by the tension roller 58 is excessive, the friction loss increases, and the timing belt 55 is basically exposed to strong stress in a non-use state where the time is overwhelmingly longer than that at the time of use. The timing belt 55 is damaged before the guaranteed endurance period is reached. In order to avoid such a strong stress on the timing belt 55 and extend its life, the movement limit of the tension roller 58 when not in use is regulated by the stopper 71 as shown in FIG. It is restricted from being deformed. Incidentally, when the motor power is transmitted, tension force acts also on the slack side, so that the belt transition locus on the slack side shifts outside the belt rotation position when not in use as shown in FIG. Therefore, even if the slack side locus becomes slack due to a sudden increase or decrease in load, the tension roller 58 can adjust the tension force following the slack without any trouble. For this reason, the limit of movement of the tension roller 58 in the belt tension direction by the stopper 71 is set so as to be slightly biased toward the tight side from the circumferential position in the free state of the timing belt 55 in the stopped state. .
[0021]
As shown in FIG. 5, according to the transmission structure that transmits the motor power to the inner blade 9 via the gear group G and the winding transmission mechanism H, the rotational reaction force that is transmitted from the inner blade 9 side to the motor side when the load fluctuates. Can be absorbed by the gear group G, and therefore, the fluctuation range of the motor rotation speed due to the load fluctuation can be reduced as compared with the conventional transmission structure in which the motor power is transmitted to the inner blade only by the winding transmission mechanism. In particular, when the gear group G is configured as a reduction gear mechanism, the rotation reaction force of the motor 17 can be effectively absorbed by the gear group G and rotation fluctuations of the motor 17 can be suppressed. It is advantageous in that it is not necessary to use an output motor, the manufacturing cost of the electric razor can be reduced, and the degree of battery consumption can be reduced.
[0022]
A transmission chamber 28 is defined by a partition wall 29 of the motor base 22, a side wall 33 of the head frame 23, and a cover 34 that covers the outer surfaces of the both 29 and 33, and is detachable from the pulley shaft 60 as shown in FIG. If the flange 62 attached to the cover 34 is held by the restriction boss 63 of the cover 34 so that it cannot be detached, the entire winding transmission mechanism H is exposed only by removing the cover 34 and the timing belt 55 and the tension mechanism T are operated. It is easy to check the condition. Since the timing belt 55 can be easily separated from the driving pulley 52 by removing the flange 62 from the pulley shaft 60, the belt replacement operation after the end of the durability period can be performed easily and with less effort.
[0023]
When the roller support 57 is raised and supported by the shaft 70 integrally formed with the side wall 33 so as to be able to swing back and forth, the tension of the timing belt 55 can be effectively adjusted while minimizing the swing range of the roller support 57. Therefore, the winding transmission mechanism H can be made compact by the amount that the space occupied by the tension mechanism T in the transmission chamber 28 can be reduced. Since the shaft 70 and the stopper 72 are integrated with the side wall 33, the structure can be simplified.
[0024]
【Example】
1 to 15 show an embodiment of a water-washing type electric shaver according to the present invention. 2 to 5, the electric razor has a main body case 1 and a razor head 2 provided on the upper part thereof, a vertically long display panel 3 is provided on the front surface of the main body case 1, and a motor starting switch is provided above and below the main body case 1. A button 4, a mode switching button 5 for switching the operation mode, an indicator lamp 6 for displaying the switching state of both buttons 4 and 5, and the like are provided. As shown in FIG. 6, the rear face of the main body case 1 is provided with a squeezing blade 7 and a slide knob 8 for raising and lowering the squeezing blade 7. The razor head 2 is provided with a pair of front and rear inner blades 9 and outer blades 10 and a center blade 11.
[0025]
The main body portion below the razor head 2 has a deformed cylindrical main body case 1 whose upper and lower ends are opened, an electrical component unit 13 that is inserted and loaded into the inside from the upper surface side, and a bottom case 14 that is assembled from the lower surface side of the case. The razor head 2 is fixed to the upper part of the electrical component unit 13 via the seal 15. The electrical component unit 13 is loaded in the main body case 1, the electrical component unit 13 and the bottom case 14 fitted in the main body case 1 are fastened with screws, the previous seal 15 is brought into close contact with the inner surface of the main body case 1, Sealing the fastening portion on the bottom case 14 side with an O-ring or packing prevents water from entering the main body case 1 and enables the razor head 2 to be washed with water. The electrical component unit 2 is formed by assembling a motor 17, a secondary battery 18, a switch, an LED, a circuit board 19 on which electronic components and the like are mounted on a plastic molded inner frame 16. A watertight packing 20 is provided on the output shaft portion of the motor 17.
[0026]
In FIG. 4, the razor head 2 includes a motor base 22 to which the motor 17 is fixed, a head frame 23 formed in an inverted portal shape, an inner blade support base 24, an inner blade frame 25, and an outer blade holder 26. Etc. The inner cutter 9 is assembled to the inner cutter frame 25, and the outer cutter 10 and the center cutter 11 are assembled to the outer cutter holder 26, respectively. A first transmission chamber 27 is defined in the lower part of the razor head 2, and a second transmission chamber 28 is defined on one side thereof. Both transmission chambers 27 and 28 are partitioned in a sealed manner by a partition wall 29 as will be described later.
[0027]
The motor base 22 is composed of a frame having an upper surface surrounded by front and rear walls and left and right walls, and a motor 17 is fixed to the lower surface. As shown in FIG. 4, the left peripheral side wall is the previous partition wall 29. The motor holder 30 that is externally fitted and fixed to the lower half of the motor 17 is supported so as to be movable up and down with respect to the inner frame 16, and is further pushed up and biased by a spring 31 (see FIG. 5). That is, the entire razor head 2 is supported so as to be able to float in the front-rear, left-right, and vertical directions with respect to the inner frame 16. A space between the motor base 22 and the motor holder 30 is hermetically sealed with the previous seal 15.
[0028]
The head frame 23 has a case portion 32 that opens downward, and side walls 33 that are erected on both the left and right sides of the case portion 32, and the case portion 32 is bonded and fixed to the motor base 22 in a cover-like manner. A first transmission chamber 27 is defined between the joining surfaces 22 and 32. In this joined state, the side wall 33 and the partition wall 29 are flush with each other, and the second transmission chamber 28 is defined by both of them 29 and 33 and the cover 34 that is put on them. The cover 34 is detachably engaged with the side wall 33. The right cover 35 is provided with a release button 36 for unlocking the outer blade holder 26.
[0029]
As shown in FIG. 8, the first transmission chamber 27 has a drain port 67 and the like for discharging water that enters during washing, and is difficult to completely seal. Is inevitable to leak. In order to prevent such leakage of noise, as shown in FIG. 9, a sound insulating wall 65 protrudes from the inside of the first transmission chamber 27, specifically, the inner surface of the head frame 23, so that the gear chamber on the gear group G side is provided. 66 and the drainage port 67 side are divided by a sound insulation wall 65, and the front and rear surfaces of the first transmission chamber 27 are multiplexed with the peripheral wall 22a of the motor base 22 and the peripheral wall 23a of the head frame 23 as shown in FIG. Covering. The previous sound insulation wall 65 partitions the first transmission chamber 27 in a state of facing the partition wall 29 along the outline of the gear group G, and minimizes the space in which the gear group G is accommodated, that is, the resonance space. Therefore, gear noise caused by resonance can be reduced.
[0030]
In FIG. 4, the inner blade support 24 includes a base 24a having a section that opens upward, a pair of left and right arms 24b erected from both left and right ends, and a lid 24c that closes the upper surface opening of the base 24a. Become. By supporting the shafts provided on the left and right arms 24b on the upper portion of the side wall 33 of the head frame 23, the inner blade support base 24 is pivotally supported so that it can swing back and forth, that is, swingable relative to the head frame 23. The An inner blade frame 25 described later is detachably press-fitted and engaged between the pair of arms 24b. Inside the pedestal base 24a, a lock mechanism is provided for locking the outer blade holder 26 that is externally fitted to the inner blade support base 24 so that it cannot be removed.
[0031]
The inner blade frame 25 has a base wall 38 and a pair of side walls 39 erected on both left and right ends of the base wall 38, and a pair of front and rear inner blades 9 are rotatably supported between the upper ends of both side walls 39. is doing. A small-diameter inner blade gear 40 is fixed to the left inner blade shaft toward FIG. 4, and this gear 40 meshes with a passive gear 41 provided on the inner blade frame 25 as shown in FIG. The motor power is transmitted to the front and rear inner blades 9 at the same time. For cleaning the inner blades, a rotating brush 42 is disposed below each inner blade 9 (see FIG. 6), and the left and right ends thereof are rotatably supported by slide pieces assembled to the side wall 39.
[0032]
The power of the motor 17 is first transmitted laterally through the gear group G accommodated in the first transmission chamber 27 and then upward by the winding transmission mechanism H accommodated in the second transmission chamber 28, and the passive gear. And transmitted to the pair of front and rear inner blades 9 through the inner blade gear 40. 5 and 8, the gear group G includes four spur gears G1 to G4 that decelerate and transmit motor power, an intermediate shaft 44 that is horizontally supported by the partition wall 29, and a final gear G4 of the gear group G. And a pair of turning gears 45 and 46 provided between the two. The turning gears 45 and 46 are each bevel gears. The intermediate shaft 44 is rotatably supported by a metal bearing 61 fixed to the partition wall 29, and both ends of the intermediate shaft 44 protrude into the first and second transmission chambers 27 and 28, respectively. The turning gear 46 is fixed, and the driving pulley 52 of the winding transmission mechanism H is fixed to the other end. That is, the intermediate shaft 44 also serves as the pulley shaft 60 of the driving pulley 52. In order to prevent the gear noise generated from the gear group G from being transmitted through the first transmission chamber 27 to the second transmission chamber 28, the space between the two chambers 27 and 28 is partitioned in a sealed manner by a partition wall 29. .
[0033]
As shown in FIG. 6, two eccentric cams (rotary drive bodies) 47 and 48 are provided on the upper part of the spur gear G1 of the first stage fixed to the output shaft 17a of the motor 17, and these eccentric cams 47 are provided. 48. The vibrator 49 for the flute blade and the vibrator 50 for the center blade can be simultaneously driven to reciprocate. Note that the kirizori blade 7 inherits the previous reciprocating power only when the slide knob 8 is slid upward. As described above, when the motor power is branched by the eccentric cams 47 and 48 provided in the first stage spur gear G1 and the vibrators 49 and 50, for example, when the power is branched from a gear group rotating around the horizontal axis. In comparison, it is possible to simplify the power branching structure and prevent the internal structure of the razor head 2 from becoming complicated.
[0034]
In FIG. 10, a winding transmission mechanism H includes a driving pulley 52 fixed to a pulley shaft 60, a driven pulley 54 fixed to a final gear shaft 53, a timing belt 55 wound around both pulleys 52 and 54, and a timing. The tension mechanism T is disposed outside the slack side transition locus of the belt 55. The timing belt 55 rotates counterclockwise in FIG. 1 and transmits motor power to the inner blade 9. The previous final stage gear shaft 53 is rotatably supported by a bearing fixed to the side wall 33 and also serves as a pulley shaft 68 of the driven pulley 54.
[0035]
The driving pulley 52 and the driven pulley 54 are each made of an injection molded product made of a tough plastic material such as polyacetal or polyamide resin, and the timing belt 55 is made of a composite rubber molded product in which polyimide fibers are mixed in urethane rubber. In order to facilitate the replacement of the timing belt 55, a washer-like flange 62 having a larger diameter than the pulley 52 is detachably attached to the intermediate shaft 44 protruding from the outer surface of the driving pulley 52 as shown in FIG. Thus, the boss 63 that supports the shaft end of the pulley shaft 60 holds the flange 62 so that it cannot be removed.
[0036]
In FIG. 11, the tension mechanism T includes a roller support 57 pivotally supported by a shaft 70 provided on the side wall 33, a tension roller 58 pivotally supported at the tip of the roller support 57, and a roller It comprises a torsion coil spring 59 that swings and biases the support 57 toward the timing belt 55. The tension roller 58 circumscribes the slack side outer peripheral surface of the transition locus of the timing belt 55 and presses the slack side belt surface in the direction of deforming inward to adjust the tension of the timing belt 55. When the tension mechanism T is disposed on one side of the circumferential position of the timing belt 55, the tension mechanism T protrudes greatly on one side of the winding transmission mechanism H, and an extra storage space is required accordingly. In order to avoid such a protrusion of the tension mechanism T and minimize the space occupied by the winding transmission mechanism H including the tension mechanism T, the pulley pulley 60 on the driving side passes through the center of the pulley shaft 68 on the driven side. Arranged so as to be biased toward the tension side of the belt transition locus rather than the vertical plane, a space for accommodating the tension mechanism T is secured between the slack side transition locus of the timing belt 55 and the peripheral side wall of the transmission chamber 28. is doing.
[0037]
The tension roller 58 and the roller support 57 are unitized. Specifically, as shown in FIG. 11, a roller support 57 is constituted by a plastic arm 72 and a press-molded reinforcement plate 73, and a tension roller 58 and a reinforcement plate are provided on a roller shaft 74 provided at the protruding end of the arm 72. After inserting through 73, the tip of the roller shaft 74 is melted, and these three are used as one unit component. As shown in FIG. 13, in a state where the roller support 57 is assembled to the shaft 70, only the base end of the arm 72 is pivotally supported by the shaft 70, and the reinforcing plate 73 cannot be removed by a screw 75 screwed into the shaft 70. It is fixed. In this assembled state, the tip of the arm 72 is in contact with a shallow recess 76 provided on the side wall 33. One end of the spring 59 is in contact with the peripheral wall of the side wall 33, and the other end is in contact with the middle part of the arm 72 (see FIG. 12).
[0038]
Since the electric razor is much longer at rest than when it is in use, the timing belt 55 is exposed to stress due to the urging force of the tension mechanism T to be deformed in an unused state. There is a risk that. In order to avoid such a strong stress on the timing belt 55, the movement limit of the tension roller 58 when not in use is restricted by the stopper 71, and the timing belt 55 is prevented from being unnecessarily deformed. Specifically, as shown in FIGS. 12 and 14, the stepped portion on the periphery of the recess 76 is used as a stopper 71 as shown in FIGS. 12 and 14, and one end of the arm 72 when not in use is received by the stopper 71. The swing limit of the roller 58 is defined. The timing belt 55 at this time is slightly biased toward the belt tension side from the belt rotation position in the free state due to the pressing force of the tension roller 58, as indicated by an imaginary line in FIGS. .
[0039]
As shown by solid lines in FIGS. 10 and 12, during use such as during shaving operation or no-load operation, tension acts on the slack side of the timing belt 55. The tip of the arm 72 is separated from the stopper 71. Therefore, even if the timing belt 55 is slack, the tension roller 58 can adjust the tension force following the belt slack. At this time, even if there is some fluctuation, the transition locus on the slack side of the timing belt 55 is substantially coincident with the rotating position of the belt in the free state. That is, the biasing force of the spring 59 is set so that the transition locus during use substantially matches the belt rotation position in the free state, thereby reducing the stress acting on the timing belt 55. Further, when the load increases rapidly, the belt that has passed through the driving pulley 52 in the stretched state is released from the pulling force, and is shifted outwardly as indicated by a symbol Y in FIG. Circulate along the trajectory. At this time, the tension roller 58 is pushed back in the clockwise direction against the spring 59, but swings in the counterclockwise direction as the load decreases to absorb the slack of the belt. In other words, in the case of a sudden load, the slack of the belt can be reliably absorbed by the help of the distance of the biased portion that is closer to the tension side than the rotating position in the free state of the belt in the stopped state. Incidentally, if the tension roller 55 can be rotated only at the non-use position described above and held undisplaceable, a tension force always acts on the timing belt 55 both when it is used and when it is not used. However, as described above, if the tension roller 55 is swung during operation, the tension force acting on the timing belt 55 can be reduced at least during operation.
[0040]
The timing belt 55 is replaced every time its endurance period expires. In this case, the cover 34 is first removed from the side wall 33. In this state, as shown in FIG. 15, when the flange 62 is removed from the pulley shaft 60, the outer surface of the driving pulley 52 is opened, so that the timing belt 55 can be easily removed from the driving pulley 52. Finally, the timing belt 55 should be replaced by pulling it out above the driven pulley 54 as indicated by the arrow and removing the belt end from between the peripheral surface of the driven pulley and the wall facing this peripheral surface. The timing belt 55 can be separated from both pulleys 52 and 54. The new timing belt 55 can be attached to both pulleys 52 and 54 through the reverse procedure.
[0041]
The tension roller 58 can be supported by the roller support 57 so as to be slidable linearly or reciprocally moved along an arc. The spring 59 can be formed of a tension spring or a compression spring. If necessary, the tension mechanism T can be configured without using the tension roller 58 by pressing the slack side of the timing belt with a leaf spring bent in a partial arc shape. The motor 17 is disposed sideways, the driving pulley 52 is fixed to the output shaft 17a, and the motor power can be transmitted to the inner blade 9 only by the winding transmission mechanism H. The driven pulley 54 may be fixed to the inner blade shaft to transmit the motor power to the inner blade 9.
[0042]
In addition to the above embodiment, the present invention can also be applied to an electric shaver provided with only one inner blade 9. The inner blade support 24 and the inner blade frame 23 of the razor head 2 may be supported by the head frame 23 so as not to swing.
[Brief description of the drawings]
FIG. 1 is a longitudinal side view showing a winding transmission mechanism in a razor head.
FIG. 2 is a front perspective view of an electric razor.
FIG. 3 is an exploded front view in which only a main body case is sectioned.
FIG. 4 is an exploded front view of a razor head.
FIG. 5 is a longitudinal front view of a razor head.
6 is a cross-sectional view taken along line BB in FIG.
7 is a cross-sectional view taken along line AA in FIG.
FIG. 8 is a cross-sectional plan view of the motor base.
FIG. 9 is a transverse bottom view of the head frame.
FIG. 10 is a side view of the winding transmission mechanism during power transmission.
FIG. 11 is an exploded perspective view of a tension mechanism.
FIG. 12 is a side view showing the operation of the tension mechanism.
13 is a cross-sectional view taken along the line CC in FIG.
14 is a sectional view taken along the line DD in FIG. 1. FIG.
FIG. 15 is a perspective view showing a timing belt replacement procedure.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Main body case 2 Razor head 9 Inner blade 28 2nd transmission chamber 44 Intermediate shaft H Winding transmission mechanism T Tension mechanism

Claims (6)

The razor head (2) at the top of the main body case (1) is provided with an inner blade (9) that is driven to rotate about the horizontal axis, and a transmission chamber (28) provided on one side of the razor head (2). In addition, a winding transmission mechanism (H) for transmitting the motor power to the inner blade (9) is accommodated,
The winding transmission mechanism (H) includes a driving pulley (52) and a driven pulley (54) disposed below and above the transmission chamber (28), and a timing belt (55) wound around both pulleys (52, 54). ) and, Yes constructed out a tension mechanism arranged outside of the slack Mi side of the timing belt (55) (T),
A tension mechanism (T) includes a tension roller (58) that contacts the outer surface of the timing belt (55), a roller support (57) that rotatably supports the tension roller (58), and a tension roller (58). It consists of a spring (59) that moves and energizes,
The tension roller (58) is urged to move by a spring (59) in a direction to deform the slack side of the timing belt (55) into an indented shape,
The pulley shaft (60) of the driving pulley (52) is arranged so as to be biased toward the tension side of the timing belt (55) from the vertical plane passing through the center of the pulley shaft (68) of the driven pulley (54). ,
A rotary electric shaver in which the roller support (57) is disposed between the slack side of the timing belt (55) and the peripheral wall of the transmission chamber (28) . A tension roller (58) is rotatably supported at one end of the roller support (57),
Roller support (57) is swingably supported by a shaft (70) provided in the power transmission chamber (28), according to claim 1, towards a spring (59) to the timing belt (55) are biases rocking The described rotary electric shaver. A stopper (71) for restricting movement of the tension roller (58) in the belt tension direction is provided on the peripheral wall of the transmission chamber (28),
The limit of movement of the tension roller (58) in the belt tension direction by the stopper (71) is biased toward the tight side of the timing belt (55) from the rotation position of the timing belt (55) in the free state in the stopped state. the rotary electric shaver according to claim 1 or 2, wherein is set to. A gear group (G) for transmitting motor power to the winding transmission mechanism (H) is accommodated in a transmission chamber (27) provided at the lower part of the razor head (2),
The transmission chamber (27) for accommodating the gear group (G) and the transmission chamber (28) for accommodating the winding transmission mechanism (H) are hermetically sealed by a partition wall (29) provided between both chambers (27, 28). Are divided into
A gear group (G) is provided between a plurality of spur gears (G1 to G4) that decelerates and transmits motor power, and a final gear (G4) and an intermediate shaft (44) of the gear group (G). And a pair of turning gears (45, 46) for converting the rotational power of the final gear (G4) into rotational power around the intermediate shaft (44),
The rotary electric shaver according to claim 1, 2 or 3 , wherein a driving pulley (52) is fixed to an intermediate shaft (44) passing through the partition wall (29) . The transmission chamber (28) is partitioned by a partition wall (29) of the motor base (22) and a side wall (33) of the head frame (23), and a cover (34) covering the outer surfaces of the partition wall (29) and the side wall (33). Has been
A flange (62) for restricting the axial movement of the timing belt (55) is detachably attached to the pulley shaft (60) protruding from the outer surface of the driving pulley (52) and provided on the inner surface of the cover (34). 5. The rotary electric shaver according to claim 1, 2 , 3 or 4 , which is held in contact with the regulating boss (63) so as not to come off . The shaft (70) is integrally projected on the outer surface of the side wall (33) defining the transmission chamber (28),
Driving pulley 52 and the roller support disposed between the driven pulley (54) (57), any one of the shaft (70) in claim 2 that is swingably upright supporting longitudinal 5 Rotary electric razor as described in 1 .

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